JPH11321360A - Lubricating structure for power transmission device for vehicle - Google Patents
Lubricating structure for power transmission device for vehicleInfo
- Publication number
- JPH11321360A JPH11321360A JP10133887A JP13388798A JPH11321360A JP H11321360 A JPH11321360 A JP H11321360A JP 10133887 A JP10133887 A JP 10133887A JP 13388798 A JP13388798 A JP 13388798A JP H11321360 A JPH11321360 A JP H11321360A
- Authority
- JP
- Japan
- Prior art keywords
- lubricating liquid
- vehicle
- lubricant
- lubricating
- power transmission
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Arrangement Of Transmissions (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、車両の動力伝達装
置に使用する長尺の回転軸を支持する軸受の潤滑を車体
の傾斜にかかわらず良好に行うことができるようにした
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubrication system for a bearing for supporting a long rotating shaft used in a power transmission device of a vehicle, regardless of the inclination of the vehicle body.
【０００２】[0002]
【従来の技術】従来の車両用動力伝達装置の潤滑構造と
しては、例えば図３に示すファイナルドライブに適用し
たものがある。2. Description of the Related Art As a conventional lubrication structure for a vehicle power transmission device, there is a lubrication structure applied to, for example, a final drive shown in FIG.
【０００３】この従来例は、前後方向に延長するケース
体１００内の後端側にデファレンシャルギヤを内装した
デフケース１０１が配設され、このデフケース１０１の
ドライブギヤ１０２に長尺のドライブピニオン１０３が
噛合され、このドライブピニオン１０３の回転軸が前方
に延長されて、その前端部がコンパニオンフランジ１０
４を介して前輪側に配設されたトランスファにプロペラ
シャフトを介して連結されるように構成されている。In this conventional example, a differential case 101 having a differential gear therein is disposed at a rear end side of a case body 100 extending in the front-rear direction. The drive shaft of the drive pinion 103 is extended forward, and the front end thereof is connected to the companion flange 10.
4 to be connected to a transfer disposed on the front wheel side via a propeller shaft.
【０００４】ここで、ドライブピニオン１０３は、長尺
であるため、そのデフケース１０１側で所定間隔を保っ
た２つの円錐ころ軸受１０５及び１０６によってケース
体１００に回転自在に支持されると共に、前端側で内部
にグリースを充填したシール形玉軸受１０７によって回
転自在に支持されている。Since the drive pinion 103 is long, the drive pinion 103 is rotatably supported on the case body 100 by two tapered roller bearings 105 and 106 at a predetermined interval on the differential case 101 side, and at the front end side. And is rotatably supported by a sealed ball bearing 107 filled with grease.
【０００５】このように、前端側の玉軸受１０７につい
てはシール形を適用している理由は以下のとおりであ
る。すなわち、ケース体１００内に潤滑液が注入されて
いるが、その潤滑液面は通常車体が水平状態である状態
でドライブピニオン１０３の中心軸線より下側となって
おり、この車体水平状態では、円錐ころ軸受１０５及び
１０６、及び玉軸受１０７の下端側が潤滑液内に浸漬さ
れることにより、良好な潤滑状態を確保することができ
る。The reason why the seal type is applied to the front end side ball bearing 107 is as follows. That is, although the lubricating liquid is injected into the case body 100, the lubricating liquid level is generally lower than the center axis of the drive pinion 103 in a state where the vehicle body is in a horizontal state. By immersing the lower end sides of the tapered roller bearings 105 and 106 and the ball bearing 107 in the lubricating liquid, a favorable lubricating state can be ensured.
【０００６】ところが、車両が勾配の急な上り坂を走行
する状態となると、車体が後ろ下がりに傾斜する後傾状
態となることにより、前端側の玉軸受１０７は潤滑液面
より上方に浮き上がって潤滑液とは非接触状態となっ
て、玉軸受１０７に対する潤滑が困難となることを考慮
し、この車体が後傾状態での前端側の玉軸受１０７の潤
滑を確保するためにシールでグリースを封入したシール
形軸受を採用するようにしている。However, when the vehicle travels on a steep uphill, the vehicle body is in a rearwardly inclined state in which the vehicle body is inclined backward and downward, and the ball bearing 107 on the front end side rises above the lubricating liquid level. Considering that the lubricant does not come into contact with the lubricating liquid and lubrication of the ball bearings 107 becomes difficult, grease is applied with a seal to secure the lubrication of the front end ball bearings 107 when the vehicle body is tilted rearward. Sealed bearings are used.
【０００７】なお、車両が勾配の急な下り坂を走行する
場合には、潤滑液面が傾斜することになるが、ケース体
１００の前端側の容積がデフケース１０１を含む後端側
の容積に比べて小さいので、潤滑液がケース体１００の
後端側に集まることにより、車体の前傾状態にもかかわ
らず、潤滑液面はさほど低下せず、後端側の円錐ころ軸
受１０５は潤滑剤内に浸漬しており、十分な潤滑を確保
することができる。When the vehicle travels on a steep downhill, the lubricating fluid level is inclined. However, the volume of the front end of the case body 100 is reduced to the volume of the rear end including the differential case 101. Since the lubricating liquid is collected at the rear end side of the case body 100, the lubricating liquid level does not decrease so much despite the forward leaning state of the vehicle body. It is immersed inside, and sufficient lubrication can be secured.
【０００８】[0008]
【発明が解決しようとする課題】しかしながら、上記従
来例にあっては、長尺のドライブピニオン１０３をケー
ス体１００に回転自在に支持するために、３つの軸受を
必要とするので、コストが嵩むと共に、車体重量も増加
することになり、さらに車体傾斜時に潤滑液面から浮き
上がる軸受については高価なシール形を適用する必要が
あるため、よりコストが嵩むという未解決の課題があ
る。However, in the above conventional example, three bearings are required to rotatably support the long drive pinion 103 on the case body 100, so that the cost increases. At the same time, the weight of the vehicle body also increases, and an expensive seal type must be applied to the bearing that floats from the lubricating liquid level when the vehicle body is tilted. Therefore, there is an unsolved problem that the cost increases.
【０００９】そこで、本発明は、上記従来例の未解決の
課題に着目してなされたものであり、車体傾斜時に潤滑
液面から浮き上がる軸受に対して良好な潤滑を行うこと
を可能として、コストを低下させると共に、車体重量の
軽量化に寄与することができる動力伝達装置の潤滑構造
を提供することを目的としている。Accordingly, the present invention has been made in view of the above-mentioned unsolved problems of the prior art, and is capable of performing good lubrication for a bearing floating from a lubricating fluid level when the vehicle body is tilted, thereby reducing cost. It is an object of the present invention to provide a lubrication structure for a power transmission device that can reduce the vehicle weight and contribute to reducing the weight of the vehicle body.
【００１０】[0010]
【課題を解決するための手段】上記目的を達成するため
に、本発明の請求項１に係る動力伝達装置の潤滑構造
は、車体の前後方向又は左右方向に延長する長尺の回転
軸を少なくとも２つの軸受を介してケース体に支持する
ようにした車両用動力伝達装置において、前記ケース体
に前記回転軸を前後２つの軸受を介して支持し、前記ケ
ース体内周面に車体の前後方向又は左右方向の傾斜時に
ケース体内に注入された潤滑液面から上方に浮き上がる
軸受に対して潤滑液を供給する潤滑液溝を形成すると共
に、前記回転軸に前記潤滑液溝に対して潤滑液を供給す
る潤滑液供給部材が形成されていることを特徴としてい
る。In order to achieve the above object, a lubricating structure for a power transmission according to claim 1 of the present invention comprises a long rotating shaft extending in the front-rear direction or the left-right direction of the vehicle body. In a vehicle power transmission device configured to be supported on a case body via two bearings, the case body supports the rotation shaft via two front and rear bearings, and a front or rear direction of a vehicle body on the peripheral surface of the case body. Forming a lubricating groove for supplying a lubricating liquid to a bearing floating upward from a surface of the lubricating liquid injected into the case body when tilting in the left-right direction, and supplying a lubricating liquid to the lubricating groove on the rotating shaft; A lubricating liquid supply member is formed.
【００１１】この請求項１に係る発明においては、車体
が傾斜して潤滑液面から上方に浮き上がる軸受に対して
ケース体内周面に潤滑液溝が形成され、この潤滑液溝に
対して回転軸に形成された潤滑液供給部材によって潤滑
液が供給されるので、車体が傾斜して潤滑液面から浮き
上がった軸受に対して潤滑液供給部材によって潤滑液溝
に供給された潤滑液が潤滑液溝を伝って潤滑液面から浮
き上がった軸受に対して供給されることにより、この軸
受の潤滑を確保する。According to the first aspect of the present invention, a lubricating groove is formed on the inner peripheral surface of the case with respect to the bearing in which the vehicle body is inclined and floats upward from the lubricating liquid surface. Since the lubricating liquid is supplied by the lubricating liquid supply member formed in the lubricating liquid groove, the lubricating liquid supplied to the lubricating liquid groove by the lubricating liquid supplying member is supplied to the lubricating groove by the lubricating liquid supplying member with respect to the bearing in which the vehicle body tilts and floats from the lubricating liquid surface. The lubrication of this bearing is ensured by being supplied to the bearing that has floated from the lubricating liquid level through the bearing.
【００１２】また、請求項２に係る動力伝達装置の潤滑
構造は、請求項１の発明において、前記潤滑液溝の傾斜
角が、車両安定限界傾斜角以上に設定されていることを
特徴としている。According to a second aspect of the present invention, the lubricating structure of the power transmission device is characterized in that, in the first aspect of the present invention, the inclination angle of the lubricating liquid groove is set to be equal to or greater than the vehicle stability limit inclination angle. .
【００１３】この請求項２に係る発明においては、潤滑
液溝の傾斜角が車両安定限界傾斜角以上に設定されてい
ることにより、通常の車両走行での車体傾斜状態で確実
に潤滑液を軸受に供給することができる。According to the second aspect of the present invention, since the inclination angle of the lubrication liquid groove is set to be equal to or larger than the vehicle stability limit inclination angle, the lubricating liquid can be reliably supplied to the vehicle in a state where the vehicle body is inclined during normal vehicle running. Can be supplied to
【００１４】さらに、請求項３に係る動力伝達装置の潤
滑構造は、請求項１又は２の発明において、前記潤滑液
供給部材は、回転軸に形成された潤滑液掻上用リングで
構成されていることを特徴としている。According to a third aspect of the present invention, in the lubricating structure for a power transmission device according to the first or second aspect, the lubricating liquid supply member is constituted by a lubricating liquid scraping ring formed on a rotating shaft. It is characterized by having.
【００１５】この請求項３に係る発明においては、回転
軸に形成された潤滑液掻上用リングが潤滑液に浸漬され
て回転することにより、その回転に応じて潤滑液が掻上
られることにより、潤滑液溝に潤滑液を確実に供給する
ことができる。In the invention according to the third aspect, the lubricating liquid scooping ring formed on the rotating shaft is immersed in the lubricating liquid and rotates, whereby the lubricating liquid is scooped in accordance with the rotation. The lubricating liquid can be reliably supplied to the lubricating liquid groove.
【００１６】さらにまた、請求項４に係る動力伝達装置
の潤滑構造は、請求項１乃至請求項３の何れかの発明に
おいて、前記回転軸は、前輪側駆動を基準とする四輪駆
動車のトランスファに使用される後輪側のドライブピニ
オンで構成されていることを特徴としている。According to a fourth aspect of the present invention, there is provided a lubricating structure for a power transmission device according to any one of the first to third aspects, wherein the rotating shaft is a four-wheel drive vehicle based on front-wheel drive. It is characterized by comprising a rear wheel drive pinion used for transfer.
【００１７】この請求項４に係る発明においては、前輪
側に配設される長尺のドライブピニオンを支持する２つ
の軸受の潤滑状態を車体の傾斜にかかわらず確保するこ
とができる。In the invention according to the fourth aspect, the lubrication state of the two bearings supporting the long drive pinion disposed on the front wheel side can be ensured regardless of the inclination of the vehicle body.
【００１８】[0018]
【発明の効果】請求項１に係る発明によれば、潤滑液溝
と潤滑液供給部材とを設けるだけで、車体の傾斜により
潤滑液面より上方に浮き上がる軸受に対して潤滑液を供
給することができ、円滑な潤滑状態を確保することがで
き、長尺の回転軸であっても両端側の二箇所に軸受を設
けるだけでよく、軸受数を減少させることができるの
で、コストを低減させることができるとともに車体重量
を軽量化することができ、さらに高価なシール形軸受を
使用する必要がなく、コストをより低減させることがで
きるという効果が得られる。According to the first aspect of the present invention, the lubricating fluid is supplied to the bearing floating above the lubricating fluid level due to the inclination of the vehicle body only by providing the lubricating fluid groove and the lubricating fluid supply member. It is possible to ensure a smooth lubricating state, and it is only necessary to provide bearings at two places on both ends, even for a long rotating shaft, so that the number of bearings can be reduced, thereby reducing costs. In addition, the weight of the vehicle body can be reduced, and it is not necessary to use an expensive sealed bearing, and the cost can be further reduced.
【００１９】また、請求項２に係る発明によれば、潤滑
液溝の傾斜角が車両安定限界傾斜角以上に設定されてい
るので、通常の車両走行での車体傾斜状態で確実に潤滑
液を軸受に供給することができるという効果が得られ
る。According to the second aspect of the present invention, since the inclination angle of the lubrication liquid groove is set to be equal to or larger than the vehicle stability limit inclination angle, the lubricating liquid can be surely supplied in a state where the vehicle body is inclined during normal vehicle running. The effect of being able to supply to the bearing is obtained.
【００２０】さらに、請求項３に係る発明によれば、回
転軸に形成された潤滑液掻上用リングが潤滑液に浸漬さ
れて回転することにより、その回転に応じて潤滑液が掻
上られることにより、潤滑液溝に潤滑液を確実に供給す
ることができ、回転軸にたいして大きな負荷を与えるこ
となく、潤滑液溝に潤滑液の供給を行うことができると
いう効果が得られる。Further, according to the third aspect of the invention, the lubricating liquid scooping ring formed on the rotating shaft is immersed in the lubricating liquid and rotates, so that the lubricating liquid is scooped in accordance with the rotation. Thus, the lubricating liquid can be reliably supplied to the lubricating liquid groove, and the lubricating liquid can be supplied to the lubricating liquid groove without applying a large load to the rotating shaft.
【００２１】さらにまた、請求項４に係る発明によれ
ば、前輪側に配設される長尺のドライブピニオンを支持
する２つの軸受の潤滑状態を車体の傾斜にかかわらず確
保することができるという効果が得られる。Further, according to the invention of claim 4, it is possible to ensure the lubrication state of the two bearings supporting the long drive pinion disposed on the front wheel side regardless of the inclination of the vehicle body. The effect is obtained.
【００２２】[0022]
【発明の実施の形態】以下、本発明の実施の形態を図面
に基づいて説明する。図１は、本発明を前輪駆動をベー
スとした四輪駆動車のトランスファに適用した場合の一
実施形態を示す横断面図である。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view showing an embodiment in which the present invention is applied to a transfer of a four-wheel drive vehicle based on front wheel drive.
【００２３】図中、１は前輪側に配設されたトランスフ
ァであって、このトランスファ１は、前後方向に延長す
るハウジング２内に配設された、図示しないセンタデフ
からの動力が伝達される入力回転軸３と、この入力回転
軸３に取付けられたハイポイドギヤ４に噛合し後方に延
長する長尺の回転軸としてのドライブピニオン５と、こ
のドライブピニオン５の後端側に配設された図示しない
後輪側の終減速装置にプロペラシャフトを介して連結さ
れるビスカスカップリング６とを備えた構成を有する。In FIG. 1, reference numeral 1 denotes a transfer disposed on the front wheel side. The transfer 1 is provided with an input for transmitting power from a center differential (not shown) disposed in a housing 2 extending in the front-rear direction. A rotating shaft 3, a drive pinion 5 as a long rotating shaft that meshes with a hypoid gear 4 attached to the input rotating shaft 3 and extends rearward, and a rear end side of the drive pinion 5 (not shown) It has a configuration provided with a viscous coupling 6 connected to the rear wheel-side final reduction gear via a propeller shaft.
【００２４】ここで、ハウジング２は、入力回転軸２を
支持するケース体２ａと、ドライブピニオン５を支持す
るケース体２ｂとビスカスカップリング６を支持するケ
ース体２ｃとに分割され、これらがボルト締めによって
連結されている。Here, the housing 2 is divided into a case 2a for supporting the input rotary shaft 2, a case 2b for supporting the drive pinion 5, and a case 2c for supporting the viscous coupling 6, and these are bolted. They are connected by tightening.
【００２５】また、ドライブピニオン５は、ピニオン５
ａとこれに一体に連結されたシャフト５ｂとで構成さ
れ、シャフト５ｂはピニオン５ａ側の大径部５ｃと後端
側の小径部５ｄとを有する。The drive pinion 5 includes a pinion 5
and a shaft 5b integrally connected to the shaft 5a. The shaft 5b has a large-diameter portion 5c on the pinion 5a side and a small-diameter portion 5d on the rear end side.
【００２６】そして、ドライブピニオン５は、その大径
部５ｃの前端側及び小径部５ｄの後端側を夫々ケース体
２ｂの内周面の前端部及び後端部に夫々装着された円錐
ころ軸受８及び９の内輪内に挿通することにより、ケー
ス体２ｂに回転自在に支持され、小径部５ｄの外周面に
おける大径部５ｃとの段差部及び円錐ころ軸受９の内輪
の前端面との間に前後方向の中央部が外方に膨出したス
ペーサ１０が装着されている。The drive pinion 5 has tapered roller bearings in which the front end of the large diameter portion 5c and the rear end of the small diameter portion 5d are respectively mounted on the front end and the rear end of the inner peripheral surface of the case body 2b. 8 and 9 are rotatably supported by the case body 2b by being inserted into the inner rings of the inner ring of the tapered roller bearing 9 and the stepped portion with the large diameter portion 5c on the outer peripheral surface of the small diameter portion 5d. A spacer 10 whose central portion in the front-rear direction bulges outward is mounted on the front side.
【００２７】また、ケース体２ｂの内周面には、図２の
拡大縦断面図に示すように、前後方向に延長する中心軸
線ＬC に対して所定角度θをもって前上がりに傾斜する
傾斜線ＬA に沿って延長する潤滑液溝１１が穿設され、
この潤滑液溝１１の前端はケース体２ｂの前端面側で且
つ中心軸線ＬC より上方に離間した位置に設定され、後
端側は中心軸線ＬC より下側で且つ円錐ころ軸受９の外
輪の下端側まで延長され、その後端側で幅が狭められて
いる。As shown in the enlarged vertical cross-sectional view of FIG. 2, the inner peripheral surface of the case body 2b has an inclined line that is inclined forward and upward at a predetermined angle θ with respect to a center axis L C extending in the front-rear direction. A lubricating liquid groove 11 extending along L A is provided,
The front end of the lubricating liquid groove 11 is set on the front end face side of the case body 2b and at a position spaced above the center axis L C , and the rear end side is below the center axis L C and the outer ring of the tapered roller bearing 9 , And the width is reduced at the rear end.
【００２８】ここで、潤滑液溝１１の傾斜角度θは、前
後方向の垂直面内での車両安定限界傾斜角α以上の角度
に設定するのが車体の傾斜走行状態で後端側の円錐ころ
軸受９に潤滑液を安定供給するうえで好ましい。Here, the inclination angle θ of the lubricant groove 11 is set to an angle equal to or greater than the vehicle stability limit inclination angle α in the vertical plane in the front-rear direction. This is preferable in that the lubricating liquid is stably supplied to the bearing 9.
【００２９】一方、ドライブピニオン５には、その大径
部５ｂの前後方向中央位置に円筒状の潤滑液供給部材と
しての潤滑液掻上用リング１２が装着されている。この
潤滑液掻上用リング１２はその外周面における上端の接
線が潤滑液溝１１の上面側に対向するように設定されて
いる。On the other hand, a lubricating liquid scraping ring 12 as a cylindrical lubricating liquid supply member is mounted on the drive pinion 5 at a central position in the front-rear direction of the large diameter portion 5b. The lubricating liquid scraping ring 12 is set such that a tangent at the upper end on the outer peripheral surface thereof faces the upper surface side of the lubricating liquid groove 11.
【００３０】また、ケース体２ｂの後端面にはビスカス
カップリング５の外周面に接触するシール部材１４が配
設され、潤滑液が外部に漏れることを防止している。次
に、上記実施形態の動作を説明する。A seal member 14 is provided on the rear end face of the case body 2b so as to be in contact with the outer peripheral face of the viscous coupling 5, so as to prevent the lubricating liquid from leaking to the outside. Next, the operation of the above embodiment will be described.
【００３１】今、車両が水平路面を走行しているものと
すると、ハウジング２内に充填された潤滑液の液面が図
２で実線図示の直線Ｆ１で示すように、例えば中心軸線
ＬCより僅かに下側にあるものとすると、この状態で
は、円錐ころ軸受８及び９は潤滑液内に浸漬されてお
り、ドライブピニオン５の回転に応じて円錐ころが自転
しながら公転するので、順次潤滑液に浸漬されて十分な
潤滑が行われる。[0031] Now, the vehicle is assumed to be traveling the horizontal road surface, the liquid surface of the lubricant filled in the housing 2, as indicated by the straight line F1 solid line shown in FIG. 2, for example, the central axis line L C Assuming that the tapered roller bearings are slightly lower, in this state, the tapered roller bearings 8 and 9 are immersed in the lubricating liquid, and the tapered rollers revolve while rotating by the rotation of the drive pinion 5, so that the lubrication is sequentially performed. It is immersed in the liquid to provide sufficient lubrication.
【００３２】この状態から車両が勾配の急な下り坂を走
行する状態となると、ハウジング２の前端側の容積が後
端側の容積より大きく且つ車体が前下がりの前傾姿勢と
なるので、ケース体２ｂ内の潤滑液面は図２で一点鎖線
図示の直線Ｆ２で示すように直線Ｆ１に対して時計方向
に傾斜する状態となる。When the vehicle travels on a steep downhill from this state, the volume at the front end of the housing 2 is larger than the volume at the rear end, and the vehicle body is in a forward-downward leaning posture. The level of the lubricating fluid in the body 2b is inclined clockwise with respect to the straight line F1 as shown by a straight line F2 shown by a dashed line in FIG.
【００３３】このため、前端側の円錐ころ軸受８につい
ては潤滑液内に浸漬された状態を維持するが、後端側の
円錐ころ軸受９についてはその下端側が直線Ｆ２より上
方に浮き上がって潤滑液とは非接触状態となり、自然潤
滑が絶たれることになる。For this reason, the tapered roller bearing 8 on the front end side is maintained in a state of being immersed in the lubricating liquid, but the tapered roller bearing 9 on the rear end side has its lower end floated above the straight line F2 and the lubricating liquid Is in a non-contact state, and natural lubrication is cut off.
【００３４】しかしながら、この状態では、潤滑液掻上
用リング１２が潤滑液内浸漬されていることにより、ド
ライブピニオン５の回転に伴う潤滑液掻上用リング１２
の回転によって、潤滑液が掻上げられ、掻上げられた潤
滑液が遠心力によってケース体２ｂの内周面側に吹付け
られられることにより、潤滑液溝１１内に潤滑液が供給
される。However, in this state, the lubricating liquid scraping ring 12 is rotated by the rotation of the drive pinion 5 because the lubricating liquid scraping ring 12 is immersed in the lubricating liquid.
By the rotation of, the lubricating liquid is scraped up, and the lubricating liquid thus scraped is sprayed on the inner peripheral surface side of the case body 2b by centrifugal force, so that the lubricating liquid is supplied into the lubricating liquid groove 11.
【００３５】このため、潤滑液掻上用リング１２によっ
て潤滑液溝１１内に供給された潤滑液はこの潤滑液溝１
１内を流下して後端側の円錐ころ軸受９側に流れ、この
潤滑液溝１１の後端側で溢れて円錐ころ軸受９の円錐こ
ろに供給される。For this reason, the lubricating liquid supplied into the lubricating liquid groove 11 by the lubricating liquid scooping ring 12
The lubricating liquid groove 11 is supplied to the tapered rollers of the tapered roller bearing 9 by flowing down the inside 1 and flowing toward the tapered roller bearing 9 on the rear end side.
【００３６】このとき、潤滑液溝１１の円錐ころ軸受９
の下端側が幅狭となっているので、潤滑液が溢れ易くな
り、より良好な潤滑を行うことができる。また、車体の
傾斜が少ない状態では、スペーサ１０の膨出部の外周面
が潤滑液内に浸漬されることにより、この外周面でも潤
滑液が掻上げられることになり、潤滑液溝１１への供給
潤滑液量を増加させることができる。At this time, the tapered roller bearing 9 of the lubricating liquid groove 11
Since the lower end side is narrow, the lubricating liquid easily overflows, and better lubrication can be performed. Further, in a state where the inclination of the vehicle body is small, the outer peripheral surface of the bulging portion of the spacer 10 is immersed in the lubricating liquid, so that the lubricating liquid is also scooped up on this outer peripheral surface. The amount of lubricating liquid supplied can be increased.
【００３７】このように、上記実施形態においては、前
輪側に配設したトランスファ１のドライブピニオン５
を、例えばステアリング機構のラック軸等との干渉をさ
けるために長尺とせざるを得ない場合でも、その両端を
２つの軸受８，９のみで支持することができ、軸受数を
必要最小限とすることができ、従来例に比較して、コス
トを低減することができると共に、トランスファ重量を
軽量化することができ、しかも軸受として高価なシール
形軸受を使用する必要がないので、よりコストを低減す
ることができる。As described above, in the above embodiment, the drive pinion 5 of the transfer 1 disposed on the front wheel side is provided.
For example, even if it is inevitable to be long in order to avoid interference with a rack shaft of a steering mechanism or the like, both ends thereof can be supported only by the two bearings 8 and 9 and the number of bearings can be minimized. As compared with the conventional example, the cost can be reduced, the transfer weight can be reduced, and moreover, since it is not necessary to use an expensive sealed bearing as a bearing, the cost can be further reduced. Can be reduced.
【００３８】また、潤滑液供給部材としての潤滑液掻上
用リング１２が円筒面に形成されているので、ドライブ
ピニオン５が回転しているときに大きな負荷となること
がなく、ドライブピニオン５を円滑に回転させることが
できる。Further, since the lubricating liquid scraping ring 12 as a lubricating liquid supply member is formed on a cylindrical surface, a large load is not generated when the drive pinion 5 is rotating, and the drive pinion 5 can be removed. It can be rotated smoothly.
【００３９】一方、車両が上り坂を走行する場合には、
車体が後ろ下がりの後傾姿勢となるが、この場合には、
ハウジング２の後端側の容積が前端側の容積に比較して
狭いと共に、前端側の円錐ころ軸受８の径が大きいの
で、潤滑液に浸漬されて、十分な潤滑を確保することが
できる。On the other hand, when the vehicle runs uphill,
The body will be in a backward leaning position, but in this case,
Since the volume of the rear end side of the housing 2 is smaller than the volume of the front end side, and the diameter of the tapered roller bearing 8 at the front end side is large, the housing 2 is immersed in a lubricating liquid to ensure sufficient lubrication.
【００４０】なお、上記実施形態においては、潤滑液溝
１１の傾斜角θを車両安定限界傾斜角α以上に設定する
場合について説明したが、実際上は車両安定限界傾斜角
α近傍の下り坂を走行する場合には車速を低下させるの
で、ドライブピニオン５の回転速度も低くなり、多少の
潤滑油不足が生じても大きな問題とならないので、潤滑
液溝１１の傾斜角θを車両安定限界傾斜角αより小さく
設定するようにしてもよい。In the above embodiment, the case where the inclination angle θ of the lubricant groove 11 is set to be equal to or larger than the vehicle stability limit inclination angle α has been described. When the vehicle is running, the vehicle speed is reduced, so that the rotation speed of the drive pinion 5 is also reduced. Even if a shortage of lubricating oil does not cause a serious problem, the inclination angle θ of the lubricant groove 11 is set to the vehicle stability limit inclination angle. You may make it set smaller than (alpha).
【００４１】また、上記実施形態においては、潤滑液掻
上用リング１２が円筒面に形成されている場合について
説明したが、これに限定されるものではなく、外周面に
所定ピッチで歯を形成することにより、潤滑液の掻上量
を増加させるようにしてもよい。In the above embodiment, the case where the lubricating liquid scraping ring 12 is formed on a cylindrical surface has been described. However, the present invention is not limited to this, and the teeth are formed on the outer peripheral surface at a predetermined pitch. By doing so, the scraping amount of the lubricating liquid may be increased.
【００４２】さらに、上記実施形態においては、ドライ
ブピニオン５の出力側にビスカスカップリング６を連結
した場合について説明したが、これに限定されるもので
はなく、直接プロペラシャフトを連結するようにしても
よい。Further, in the above embodiment, the case where the viscous coupling 6 is connected to the output side of the drive pinion 5 has been described. However, the present invention is not limited to this, and the propeller shaft may be directly connected. Good.
【００４３】さらにまた、上記実施形態においては、長
尺の回転軸がトランスファ１のドライブピニオン５であ
る場合について説明したが、これに限定されるものでは
なく、前述した従来例の終減速装置のドライブピニオン
にも本発明を適用することができ、さらには前後方向の
回転軸に限らず左右方向の回転軸にも本発明を適用する
ことができる。Furthermore, in the above embodiment, the case where the long rotating shaft is the drive pinion 5 of the transfer 1 has been described. However, the present invention is not limited to this. The present invention can be applied to a drive pinion. Further, the present invention can be applied to not only a front-rear rotation axis but also a left-right rotation axis.
【図１】本発明の一実施形態を示す横断面図である。FIG. 1 is a cross-sectional view showing one embodiment of the present invention.
【図２】本発明の要部を示す拡大縦断面図である。FIG. 2 is an enlarged vertical sectional view showing a main part of the present invention.
【図３】従来例を示す横断面図である。FIG. 3 is a cross-sectional view showing a conventional example.
１ トランスファ ２ ハウジング ２ａ〜２ｃ ケース体 ３ 入力回転軸 ４ ハイポイドギヤ ５ ドライブピニオン（回転軸） ５ａ ピニオン ５ｂ 大径部 ５ｃ 小径部 ８ 円錐ころ軸受 ９ 円錐ころ軸受 １１ 潤滑液溝 １２ 潤滑液掻上用リング（潤滑液供給部材） DESCRIPTION OF SYMBOLS 1 Transfer 2 Housing 2a-2c Case body 3 Input rotating shaft 4 Hypoid gear 5 Drive pinion (rotating shaft) 5a Pinion 5b Large diameter part 5c Small diameter part 8 Tapered roller bearing 9 Tapered roller bearing 11 Lubricant groove 12 Lubricating liquid ring (Lubricant supply member)
Claims (4)
長尺の回転軸を少なくとも２つの軸受を介してケース体
に支持するようにした車両用動力伝達装置において、前
記ケース体に前記回転軸を前後２つの軸受を介して支持
し、前記ケース体内周面に車体の前後方向又は左右方向
の傾斜時にケース体内に注入された潤滑液面から上方に
浮き上がる軸受に対して潤滑液を供給する潤滑液溝を形
成すると共に、前記回転軸に前記潤滑液溝に対して潤滑
液を供給する潤滑液供給部材が形成されていることを特
徴とする車両用動力伝達装置の潤滑構造。1. A power transmission device for a vehicle, wherein a long rotating shaft extending in a front-rear direction or a left-right direction of a vehicle body is supported by a case body via at least two bearings. Lubricating the bearing through the front and rear two bearings, and supplying the lubricant to the bearing that floats upward from the lubricating fluid level injected into the case when the vehicle body tilts in the front-rear direction or the left-right direction on the peripheral surface of the case. A lubricating structure for a vehicle power transmission device, wherein a lubricating liquid supply member for forming a liquid groove and supplying a lubricating liquid to the lubricating liquid groove is formed on the rotating shaft.
傾斜角以上に設定されていることを特徴とする請求項１
記載の車両用動力伝達装置の潤滑構造。2. An inclination angle of the lubricating liquid groove is set to be equal to or greater than a vehicle stability limit inclination angle.
A lubricating structure for a vehicle power transmission device according to the above.
れた潤滑液掻上用リングで構成されていることを特徴と
する請求項１又は請求項２に記載の車両用動力伝達装置
の潤滑構造。3. The power transmission device for a vehicle according to claim 1, wherein the lubricating liquid supply member is formed of a lubricating liquid scraping ring formed on a rotating shaft. Lubrication structure.
四輪駆動車のトランスファに使用される後輪側のドライ
ブピニオンで構成されていることを特徴とする請求項１
乃至請求項３の何れかに記載の車両用動力伝達装置の潤
滑構造。4. The drive shaft according to claim 1, wherein the rotating shaft comprises a rear wheel drive pinion used for transfer of a four-wheel drive vehicle based on front wheel drive.
A lubrication structure for a vehicle power transmission device according to any one of claims 3 to 3.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13388798A JP3518333B2 (en) | 1998-05-15 | 1998-05-15 | Lubrication structure of vehicle power transmission |
| US09/304,836 US6244386B1 (en) | 1998-05-15 | 1999-05-05 | Lubrication apparatus in power transmission unit |
| DE19922130A DE19922130C2 (en) | 1998-05-15 | 1999-05-12 | Lubrication device for a power transmission unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13388798A JP3518333B2 (en) | 1998-05-15 | 1998-05-15 | Lubrication structure of vehicle power transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11321360A true JPH11321360A (en) | 1999-11-24 |
| JP3518333B2 JP3518333B2 (en) | 2004-04-12 |
Family
ID=15115427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13388798A Expired - Fee Related JP3518333B2 (en) | 1998-05-15 | 1998-05-15 | Lubrication structure of vehicle power transmission |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US6244386B1 (en) |
| JP (1) | JP3518333B2 (en) |
| DE (1) | DE19922130C2 (en) |
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| JPS6117561U (en) | 1984-07-06 | 1986-02-01 | トヨタ自動車株式会社 | Lubrication mechanism of automotive final reducer |
| JPS62163829A (en) * | 1986-01-13 | 1987-07-20 | Nissan Motor Co Ltd | Four-wheel drive equipment |
| JPH0419233A (en) | 1990-05-10 | 1992-01-23 | Nissan Motor Co Ltd | Lubricating structure for vehicular power transmission device |
| DE4023354C2 (en) | 1990-07-23 | 1994-04-07 | Daimler Benz Ag | Driving axle for motor vehicles |
| SE9101962L (en) * | 1991-06-26 | 1992-12-27 | Skf Ab | TAETAT STOCK |
| US5261676A (en) * | 1991-12-04 | 1993-11-16 | Environamics Corporation | Sealing arrangement with pressure responsive diaphragm means |
| US5328275A (en) * | 1993-05-06 | 1994-07-12 | Stemco Inc. | Unitized wheel hub and bearing assembly |
| US5316106A (en) * | 1993-05-07 | 1994-05-31 | Ford Motor Company | Lubricant cooling system for a motor vehicle axle |
| US5591020A (en) * | 1994-05-19 | 1997-01-07 | Environamics Corporation | Pump oil mister |
| US5513964A (en) * | 1994-10-11 | 1996-05-07 | Environamics Corporation | Pump oil mister with reduced windage |
| US5647735A (en) * | 1994-10-11 | 1997-07-15 | Environamics Corporation | Centrifugal pump having oil misting system with pivoting blades |
| DE19538192A1 (en) * | 1995-10-13 | 1997-04-17 | Zahnradfabrik Friedrichshafen | Oil supply device for shaft bearing |
| JPH10103429A (en) * | 1996-09-30 | 1998-04-21 | Mazda Motor Corp | Gear type transmission structure |
-
1998
- 1998-05-15 JP JP13388798A patent/JP3518333B2/en not_active Expired - Fee Related
-
1999
- 1999-05-05 US US09/304,836 patent/US6244386B1/en not_active Expired - Lifetime
- 1999-05-12 DE DE19922130A patent/DE19922130C2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008089016A (en) * | 2006-09-29 | 2008-04-17 | Toyota Motor Corp | Power transmission device and vehicle |
| JP4737021B2 (en) * | 2006-09-29 | 2011-07-27 | トヨタ自動車株式会社 | Power transmission device and vehicle |
| JP2013249950A (en) * | 2012-05-30 | 2013-12-12 | Fairfield Manufacturing Co Inc | Bearing lubricating device for gear box |
| JP2020085045A (en) * | 2018-11-19 | 2020-06-04 | マツダ株式会社 | Lubrication structure of power transmission device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19922130C2 (en) | 2003-01-23 |
| JP3518333B2 (en) | 2004-04-12 |
| US6244386B1 (en) | 2001-06-12 |
| DE19922130A1 (en) | 1999-12-02 |
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